US8365764B2 - Minimum pressure valve - Google Patents

Minimum pressure valve Download PDF

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Publication number
US8365764B2
US8365764B2 US12/681,685 US68168509A US8365764B2 US 8365764 B2 US8365764 B2 US 8365764B2 US 68168509 A US68168509 A US 68168509A US 8365764 B2 US8365764 B2 US 8365764B2
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United States
Prior art keywords
bush
inlet
valve body
minimum pressure
valve
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US12/681,685
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US20100219364A1 (en
Inventor
Kristof Adrien Laura Martens
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Atlas Copco Airpower NV
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Atlas Copco Airpower NV
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Assigned to ATLAS COPCO AIRPOWER, NAAMLOZE VENNOOTSCHAP reassignment ATLAS COPCO AIRPOWER, NAAMLOZE VENNOOTSCHAP ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: MARTENS, KRISTOF ADRIEN LAURA
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K15/00—Check valves
    • F16K15/02—Check valves with guided rigid valve members
    • F16K15/025—Check valves with guided rigid valve members the valve being loaded by a spring
    • F16K15/026—Check valves with guided rigid valve members the valve being loaded by a spring the valve member being a movable body around which the medium flows when the valve is open
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K39/00—Devices for relieving the pressure on the sealing faces
    • F16K39/02—Devices for relieving the pressure on the sealing faces for lift valves
    • F16K39/022—Devices for relieving the pressure on the sealing faces for lift valves using balancing surfaces
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/3367—Larner-Johnson type valves; i.e., telescoping internal valve in expanded flow line section
    • Y10T137/3421—Line condition change responsive
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/7722—Line condition change responsive valves
    • Y10T137/7837—Direct response valves [i.e., check valve type]
    • Y10T137/785—With retarder or dashpot
    • Y10T137/7852—End of valve moves inside dashpot chamber
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/7722—Line condition change responsive valves
    • Y10T137/7837—Direct response valves [i.e., check valve type]
    • Y10T137/785—With retarder or dashpot
    • Y10T137/7852—End of valve moves inside dashpot chamber
    • Y10T137/7853—Enlarged piston on end of valve stem
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/7722—Line condition change responsive valves
    • Y10T137/7837—Direct response valves [i.e., check valve type]
    • Y10T137/7904—Reciprocating valves
    • Y10T137/7922—Spring biased
    • Y10T137/7929—Spring coaxial with valve

Definitions

  • the present invention concerns a minimum pressure valve, in particular to use at the outlet of a liquid separator of a compressor unit.
  • a minimum pressure valve which can be applied to the outlet of a liquid separator is already known, whereby this minimum pressure valve is provided with a housing with an inlet and an outlet which are connected via an inner duct system and whereby, in the above-mentioned duct system, a movable valve body is provided which is pressed against a seating round the aforesaid inlet in a first, closed position by means of a spring and thereby closes off the inlet; and whereby the valve body is situated at a distance from the above-mentioned seating in a second, open position, such that the inlet, via the duct system, is connected to the outlet.
  • the opening pressure of the minimum pressure valve can be selected as a function of the application.
  • a disadvantage of the existing minimum pressure valves is that the spring must be dimensioned such that it is capable of compensating the entire pressure force of the gas at the gas inlet.
  • pressure values may be relatively large, for example between 4 and 9 bar ( ⁇ 4.10 5 to 9.10 5 Pa) for an oil-injected compressor and even up to 20 bar ( ⁇ 20.10 5 Pa) for water-injected compressors, acting on relatively large surfaces, strong springs must be selected.
  • the overall height of the spring must be restricted so as to limit the total height of the minimum pressure valve, and to restrict the material costs and weight.
  • the opening range of the minimum pressure valve is small and that, consequently, little extra gas pressure is required to push the valve body entirely open, since the pressure drop over the minimum pressure valve is preferably as small as possible for the entire service range of the compressor (i.e. from minimum operating pressure to maximum operating pressure).
  • the valve body must reach the entirely open position as fast as possible as soon as the minimum pressure valve begins to open, in order to cause a pressure drop that is as small as possible over the entire pressure range of the compressor.
  • the aim is to further enlarge the valve opening and to make the valve lift even higher.
  • a larger valve opening i.e. larger diameter of the valve body
  • results in a considerable increase of the required spring force and consequently a more serious installation problem due to the larger spring constant, and also problems related to a high required pressure for an entirely open minimum pressure valve
  • a larger lift of the valve body moreover results in an even larger pressure range over which the valve body moves.
  • the present invention aims to provide a solution to one or several of the above-mentioned and/or other disadvantages.
  • the present invention concerns a minimum pressure valve which is provided with a housing with an inlet and an outlet which are connected via an inner duct system and whereby a movable valve body is provided in the above-mentioned duct system which is pressed against a seating round the above-mentioned inlet in a first, closed position by means of a spring and thereby closes off the inlet; and whereby the valve body is situated at a distance from the above-mentioned seating in a second, open position, such that the inlet, via the duct system, is connected to the outlet, whereby said minimum pressure valve is characterised in that the valve body is provided in a sliding manner in a valve casing which is fixed in the above-mentioned duct system and which, together with the valve body, defines a confined, inner space which is connected to the inlet via a duct which may extend for example through the valve body or which may have the shape of an external connection.
  • An advantage of such a minimum pressure valve according to the invention consists in that, thanks to the presence of the above-mentioned duct which provides for a connection between the confined space inside the valve body and the inlet, the pressure prevailing at the inlet of the minimum pressure valve can enter the space which is defined by the valve casing and the valve body, as a result of which the gas force which acts on the valve body via the inlet will be largely compensated by a gas force acting on the other side of the valve body in the opposite sense.
  • Another advantage of a minimum pressure valve according to the invention is that, as a spring with a small spring constant can be used, there is only a restricted pressure range between the initially open position and the fully opened position of the minimum pressure valve.
  • Another advantage is that the lift of the valve body can be enlarged without having to make the pressure range over which the valve body moves too large, since a spring with a small spring constant can be used.
  • valve opening can be enlarged without having to drastically alter the spring, namely by proportionally enlarging the confined inner space.
  • the above-mentioned valve casing is made in the shape of a cylinder housing defining a cylinder chamber, whereby said cylinder housing is closed on one far end by means of an end wall, and the other far end is open, and in which the valve body, via the open far end, is provided in a sliding manner with a part in the shape of a piston.
  • the above-mentioned piston is preferably made in the shape of a practically cylindrical bush in which the above-mentioned spring extends at least partly and whereby this bush is sealed on one side by means of a bottom wall through which the aforesaid duct extends. This duct can also be provided externally, however.
  • the cylinder chamber in the above-mentioned cylinder housing has a reduced diameter near its closed far end, over a certain length, whereas it has a larger diameter near the open far end of said cylinder housing.
  • the above-mentioned bush preferably also has a stepped outer surface over its length, as a first bush part has an outer diameter which practically corresponds to the reduced diameter of the cylinder chamber, and a second bush part has an outer diameter which practically corresponds to the larger diameter of the cylinder chamber.
  • the wall of the cylinder chamber between the part with the reduced diameter and the part with the larger diameter preferably has a radial collar, and on the outer perimeter of the bush is preferably also provided a radial collar between the first and the second bush part, such that a space is formed which is confined by the part of the valve casing having the larger diameter and the part of the piston having the reduced diameter as well as the respective collars of the bush and the wall, whereby this space is under atmospheric pressure. Consequently, the radial collar of the bush is the only part of the surface of the valve opposite the inlet side (i.e. the side where the spring acts on) where the pressure prevailing on the inlet side is not compensated.
  • Another advantage thereof is that a minimum pressure valve having a very large opening pressure of for example 20 bar ( ⁇ 20.10 5 Pa) can be realised by means of a light spring having a restricted pressure range during the lift of the valve body by making the surface on which the atmospheric pressure acts sufficiently small.
  • FIG. 1 schematically represents a liquid separator which is provided with a minimum pressure valve according to the invention, seen in perspective;
  • FIG. 2 shows a section according to line II-II in FIG. 1 ;
  • FIG. 3 shows the part indicated by F 3 in FIG. 2 to a larger scale.
  • the figures show a liquid separator 1 which is provided with a centrifugal separator 2 formed of a cylindrical housing 3 with an upper wall 4 and a lower wall 5 and with a tangential inlet 6 and an axial outlet 7 , which housing 3 defines an inner space 8 .
  • the above-mentioned outlet 7 is preferably provided centrally in the upper wall of the housing 3 and it is closed by means of a minimum pressure valve 9 according to the invention which forms a connection between the space 8 and a take-off point for purified gas.
  • the centrifugal separator 2 in this case also comprises a discharge orifice 10 for separated liquid, which discharge orifice 10 is preferably situated at the bottom of the centrifugal separator 2 in the mounted position of the latter, in or near the above-mentioned lower wall 5 .
  • a flow-through element 11 for example in the form of a coalescence filter or another type of fine filter, or in other words a filter which makes it possible to remove remaining drops of liquid from the gas flow.
  • the above-mentioned flow-through element 11 is made cylindrical with walls that are permeable to gas, and said flow-through element 11 is sealed on one side, i.e. the bottom side in the arrangement as represented, by means of a sealing wall 12 .
  • the top side of the above-mentioned flow-through element 11 is fixed to the upper wall 4 , and it is positioned such that this flow-through element 11 extends entirely round the above-mentioned outlet 7 .
  • the minimum pressure valve 9 consists of a housing 13 which, in this case but not necessarily, also forms the upper wall 4 of the centrifugal separator 2 and which housing 13 is provided with an inlet 14 and an outlet 15 which are connected via an inner duct system 16 .
  • a fixed valve casing 17 which is preferably made in the form of a cylinder housing 18 which is sealed on one side by means of an end wall 19 and which is open on the other side, and whereby this cylinder housing 18 defines a cylinder chamber 20 in which has been provided a valve body 21 in a sliding manner, via the open end, by means of a part in the shape of a piston 22 .
  • the above-mentioned piston 22 is preferably made in the shape of a practically cylindrical bush 23 which is sealed on one side, in the given position on the lower side or, in other words, the side opposite the inlet 14 , by means of a lower wall 24 .
  • the cylinder chamber 20 in the above-mentioned cylinder housing 18 has a first reduced diameter D 1 at its far end which is sealed by the end wall 19 , whereas it has a second, larger diameter D 2 near the open end of said cylinder housing 18 which is larger than the above-mentioned first, reduced diameter D 1 .
  • the above-mentioned bush 23 preferably has a stepped outer surface over its length as it comprises a first bush part 23 A with an outer diameter which practically corresponds to the reduced diameter D 1 of the cylinder chamber 20 , and a second bush part 23 B with an outer diameter which practically corresponds to the larger diameter D 2 of the cylinder chamber 20 .
  • the above-mentioned first bush part 23 A extends at least partly in the part of the cylinder chamber 20 with the reduced diameter D 1 , in the mounted position of the minimum pressure valve 9 , whereas the second bush part 23 B is provided in the part of the cylinder chamber 20 with the larger diameter D 2 .
  • the wall of the cylinder chamber 20 has a radial collar 25 between the part with the first diameter D 1 and the part with the second diameter D 2 , whereas a radial collar 26 is also provided on the outer perimeter of the bush 23 between the first and the second bush part 23 A, 23 B respectively.
  • a confined space 27 which is put under atmospheric pressure, for example by connecting this space 27 to the atmosphere via a small duct, not represented in the figures.
  • bush 23 extends a spring 28 which pushes with one far end against the end wall 19 of the valve casing 17 , and with its other end against the lower wall 24 of the bush 23 of the valve body 21 .
  • a sealing element 29 which, under the influence of the spring 28 , is pushed against a seating 30 round the above-mentioned inlet 14 in a first, closed position and hereby seals the inlet 14 , but which, in a second, open position of the minimum pressure valve 9 , is situated at a distance from said seating 30 , such that the inlet 14 , via the duct system 16 , is connected to the outlet 15 .
  • the sealing element 29 is in this case connected to the bush 23 by means of a valve stem 31 around which said sealing element 29 extends.
  • This valve stem 31 can be fixed to the above-mentioned bush 23 , for example by means of a press fit or the like, or it can be erected in a movable manner in the same axial direction as the piston 22 , for example by means of a loose fit, in the above-mentioned bush 23 to thus function as a non-return valve.
  • the compressed air network of the consumer which is connected to the vessel via the outlet 15 , the duct system 16 and the inlet 14 , can be kept under pressure, whereas the vessel pressure is blown off and lowered so as to switch the compressor into idle running or to even switch it off entirely.
  • the lower wall 24 is in this case provided with a central opening around which extends a cylindrical fixing wall 32 in which the valve stem 31 has been provided in a partly fixed or movable manner. If the valve stem 31 has been erected inside the cylindrical fixing wall 32 in a movable manner, a sealing will preferably be provided between both elements, which is not represented in the figure.
  • valve stem 31 In order to axially lock the sealing element 29 in relation to the valve stem 31 , the valve stem 31 is provided with a stop-forming collar 33 against which the sealing element 29 is pressed by means of fixing means provided to that end which in this case comprise a nut 34 which is screwed round the free end of the valve stem 31 .
  • the above-mentioned nut 34 preferably has an aerodynamic shape, in other words a shape which hinders the flow from the centrifugal separator 2 into the duct system 16 as little as possible.
  • a duct 35 extends through the valve body 21 which connects the inlet 14 to a confined, inner space 36 which is defined by the valve body 21 and the valve casing 17 .
  • the duct 35 in this case extends through the valve stem 31 , the sealing element 29 and the bush 23 .
  • This connection between the inlet 14 and the inner space 36 can also be provided externally, however.
  • the inlet 14 of the minimum pressure valve 9 has a surface which is slightly larger than the total axially directed surface of the valve body 21 on the side of the valve body 21 turned towards the end wall 19 , which is possible in this case as the diameter of the inlet 14 is larger than the above-mentioned first, reduced diameter D 1 of the cylinder chamber 20 .
  • the total, axially directed surface of the lower wall 24 is smaller than the flow-through surface of the inlet 14 , whereby by flow-through surface is meant the surface in a plane which is directed crosswise to the direction of movement of the valve body 21 .
  • a mixture of compressed gas and liquid such as a mixture of compressed air and drops of liquid coming from a liquid-injected compressor element, enters into the space 8 via the inlet 6 .
  • the separated liquid drips via the cylindrical wall to the lower side of the centrifugal separator 2 , where said liquid is discharged via the discharge orifice 10 .
  • the purified gas flows through the minimum pressure valve 9 to be taken off by a user.
  • the pressure which is built up in the centrifugal separator 2 and thus at the inlet 14 is also built up in the space 36 between the valve body 21 and the valve casing 17 , such that the gas forces acting as of the space 8 on the sealing element 29 are largely compensated by opposite gas forces acting as of the space 36 on the bush 23 , and in particular on its lower wall 24 .
  • the spring 28 makes sure that, in the given position of the minimum pressure valve 9 , an additional downward force is exerted on the valve body 21 .
  • valve body 21 Only the outer stage of the valve body 21 , i.e. the space 27 , is connected to the atmospheric pressure, such that a difference in compressive force is obtained at the top side of the valve body 21 (downstream) and at the bottom side of the valve body 21 (upstream).
  • the surface of the sealing element 29 which is turned towards the inlet 14 is larger than the total axially directed surface of the first bush part 23 A situated opposite the end wall 19 of the valve casing 17 .
  • the sealing element 29 will be pushed off the seating 30 , as the upward gas forces acting on said sealing element 29 become larger than the sum of the downward directed gas forces and the spring force.
  • the opening pressure of the minimum pressure valve 9 may have a high pressure value of for example 4 to 9 bar ( ⁇ 4.10 5 to 9.10 5 Pa) or even up to 20 bar ( ⁇ 20.10 5 Pa) in the case of water-injected compressors, without any expensive spring with a large spring constant having to be provided.
  • the opening range of the pressure is considerably smaller than with the existing minimum pressure valves 9 which do not have any compensation of forces in the form of a counterpressure acting on the valve body 21 as of the cylinder chamber 20 .
US12/681,685 2008-03-27 2009-03-19 Minimum pressure valve Active 2030-02-22 US8365764B2 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
BE2008/0186 2008-03-27
BE2008/0186A BE1018073A3 (nl) 2008-03-27 2008-03-27 Minimum-drukventiel.
PCT/BE2009/000017 WO2009117788A1 (en) 2008-03-27 2009-03-19 Minimum pressure valve

Publications (2)

Publication Number Publication Date
US20100219364A1 US20100219364A1 (en) 2010-09-02
US8365764B2 true US8365764B2 (en) 2013-02-05

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Family Applications (1)

Application Number Title Priority Date Filing Date
US12/681,685 Active 2030-02-22 US8365764B2 (en) 2008-03-27 2009-03-19 Minimum pressure valve

Country Status (16)

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US (1) US8365764B2 (da)
EP (1) EP2255112B1 (da)
JP (1) JP5296190B2 (da)
CN (1) CN101836020B (da)
BE (1) BE1018073A3 (da)
BR (1) BRPI0905872B1 (da)
CA (1) CA2697676C (da)
CY (1) CY1115515T1 (da)
DK (1) DK2255112T3 (da)
ES (1) ES2507087T3 (da)
HU (1) HUE021936T2 (da)
PL (1) PL2255112T3 (da)
PT (1) PT2255112E (da)
RU (1) RU2477405C2 (da)
SI (1) SI2255112T1 (da)
WO (1) WO2009117788A1 (da)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102563157B (zh) * 2011-10-08 2014-04-16 张周卫 中流式低温过程控制减压节流阀
BE1025384B1 (nl) * 2017-07-07 2019-02-11 Atlas Copco Airpower Naamloze Vennootschap Een minimumdrukregelklep en compressor omvattende een dergelijke minimumdrukregelklep
BE1026140B1 (nl) * 2018-03-27 2019-10-29 Atlas Copco Airpower Naamloze Vennootschap Verbeterd minimum drukventiel en werkwijze voor onderhoud van dergelijk ventiel
RU2735121C2 (ru) * 2018-10-05 2020-10-28 Юрий Николаевич Скрипов Самодействующий клапан
RU193252U1 (ru) * 2019-08-15 2019-10-21 Акционерное общество "Машиностроительный завод "Армалит" Клапан обратный

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US3053439A (en) * 1957-07-24 1962-09-11 Leybolds Nachfolger E Rotary vacuum pump
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GB2295442A (en) 1994-11-04 1996-05-29 Rc Subsea As Throttle valve
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EP1614945A1 (de) 2004-07-08 2006-01-11 INA-Schaeffler KG Rückschlagventil
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CA2697676C (en) 2014-09-09
PT2255112E (pt) 2014-07-30
RU2477405C2 (ru) 2013-03-10
JP5296190B2 (ja) 2013-09-25
CA2697676A1 (en) 2009-10-01
BRPI0905872B1 (pt) 2020-03-10
CN101836020B (zh) 2012-11-14
DK2255112T3 (da) 2014-09-29
US20100219364A1 (en) 2010-09-02
PL2255112T3 (pl) 2014-11-28
WO2009117788A8 (en) 2009-12-10
EP2255112A1 (en) 2010-12-01
CY1115515T1 (el) 2017-01-04
JP2011517484A (ja) 2011-06-09
ES2507087T3 (es) 2014-10-14
HUE021936T2 (hu) 2021-12-28
WO2009117788A1 (en) 2009-10-01
BRPI0905872A2 (pt) 2015-06-30
BE1018073A3 (nl) 2010-04-06
EP2255112B1 (en) 2014-06-25
SI2255112T1 (sl) 2014-10-30
CN101836020A (zh) 2010-09-15

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